EP1088991A1 - Compresseur sans embrayage du type a plateau oscillant a deplacement variable - Google Patents

Compresseur sans embrayage du type a plateau oscillant a deplacement variable Download PDF

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Publication number
EP1088991A1
EP1088991A1 EP99925334A EP99925334A EP1088991A1 EP 1088991 A1 EP1088991 A1 EP 1088991A1 EP 99925334 A EP99925334 A EP 99925334A EP 99925334 A EP99925334 A EP 99925334A EP 1088991 A1 EP1088991 A1 EP 1088991A1
Authority
EP
European Patent Office
Prior art keywords
passage
pressure
swash plate
crankcase
refrigerant gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP99925334A
Other languages
German (de)
English (en)
Inventor
Yukio Zexel Corporation Kounan-works KAZAHAYA
Shoichi Zexel Corporation Kounan-works KIDO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Thermal Systems Japan Corp
Original Assignee
Bosch Automotive Systems Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bosch Automotive Systems Corp filed Critical Bosch Automotive Systems Corp
Publication of EP1088991A1 publication Critical patent/EP1088991A1/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/185—Discharge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1854—External parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
    • F04B2027/1872—Discharge pressure

Definitions

  • This invention relates to a clutchless variable capacity swash plate compressor to which a driving force is constantly transmitted e.g. from an engine, and more particularly to a clutchless variable capacity swash plate compressor of this kind which is capable of preventing high-pressure refrigerant gas from flowing out into a condenser especially under an extremely low-load operating condition of the compressor and circulating the refrigerant gas within the compressor, thereby reducing refrigerating capacity to zero.
  • Conventional clutchless compressors includes a clutchless variable capacity swash plate compressor.
  • the inclination angle of a swash plate thereof changes according to a suction pressure to thereby change a length of piston stroke for increasing or decreasing the delivery quantity of the compressor.
  • the inclination angle of a swash plate thereof becomes smaller with decrease in thermal load, whereby the swash plate urges a transmission cylinder toward the rear of the compressor to cause the transmission cylinder to urge a blocking member toward the rear of the compressor.
  • the blocking member closes a suction passage to inhibit low-pressure refrigerant gas from flowing in from an evaporator.
  • a control valve allows communication between a discharge chamber and a crankcase, whereby high-pressure refrigerant gas flows from the discharge chamber to the crankcase, and a flow of the refrigerant gas toward a condenser is substantially inhibited.
  • the transmission cylinder and the blocking member for closing the suction passage are mounted on a rotational shaft, it is required to arrange the discharge chamber at a location radially outward of a suction chamber within a cylinder head, which makes it difficult to ensure reliable control of sealing of the compressor against the outside air. For instance, enhanced machining accuracy, proper fastening torque for fastening bolts (i.e. bolts for combining a cylinder block and a cylinder head), and so forth are required for the purpose.
  • the rotational shaft is preloaded by a spring via the transmission cylinder, bearings, and the blocking member, which makes it impossible to apply sufficient preload to the rotational shaft.
  • the rotational shaft and rotary support members are not stable in the axial direction, which increases noise due to vibration.
  • the spring for urging the blocking member expands, thereby causing a further increase in noise.
  • the spring for urging the blocking member is rotated together with the blocking member, so that the spring can be wrung off, making it impossible to open or close the suction passage.
  • a clutchless variable capacity swash plate compressor comprising: a swash plate slidably and tiltably fitted on a rotational shaft, for rotation in unison with the rotational shaft, a crankcase in which the swash plate is received, a suction chamber for receiving refrigerant gas to be sent to a compression chamber, a first passage for guiding the refrigerant gas from the crankcase to the suction chamber, the first passage having a cross-sectional area which is reduced by the swash plate when an inclination angle of the swash plate is minimum, a discharge chamber for receiving the refrigerant gas delivered from the compression chamber, a discharge port via which the refrigerant gas is discharged from the discharge chamber toward a condenser, a refrigerant outlet passage for guiding the refrigerant gas from the discharge chamber to the discharge port, a second passage for guiding the refrigerant gas from the discharge chamber to the crankcase, a pressure
  • the suction chamber can be arranged at a location radially outward of the discharge chamber within a housing, which facilitates control of sealing of the compressor against the outside air. Further, it is possible to avoid the event that the spring for preloading the rotational shaft is wrung off by being freely rotated following the rotation of the rotational shaft, making it impossible to opening/closing the suction port, so that the reliability of the compressor is enhanced. However, since sufficient preload can be applied to the rotational shaft, it is possible to make the same stable in the axial direction, thereby reducing noise due to vibration.
  • the discharge control valve is a check valve.
  • a first orifice is formed in an intermediate portion of the third passage, a passage area of the first orifice being smaller than a passage area of a second orifice formed in an intermediate portion of the first passage.
  • the function of guiding the refrigerant, gas from the crankcase to the suction chamber through the third passage only when the cross-sectional area of the first passage is reduced by the swash plate can be realized by a simple construction.
  • a clutchless variable capacity swash plate compressor comprising: a swash plate slidably and tiltably fitted on a rotational shaft, for rotation in unison with the rotational shaft, a crankcase in which the swash plate is received, a suction chamber for receiving refrigerant gas to be sent to a compression chamber, a first passage for guiding the refrigerant gas from the crankcase to the suction chamber, the first passage having a cross-sectional area which is reduced by the swash plate when an inclination angle of the swash plate is minimum, a discharge chamber for receiving the refrigerant gas delivered from the compression chamber, a discharge port via which the refrigerant gas is discharged from the discharge chamber toward a condenser, a refrigerant outlet passage for guiding the refrigerant gas from the discharge chamber to the discharge port, a second passage for guiding the refrigerant gas from the discharge chamber to the crankcase, a pressure control valve arranged in an
  • the refrigerant gas in the discharge chamber is directly introduced to the discharge control valve to drive the same, the responsivity of the discharge control valve is improved.
  • the delivery quantity of the refrigerant gas i.e. the capacity of the compressor
  • the capacity of the compressor can be changed promptly, which makes it possible to obtain a more agreeable air-conditioned state by cooling.
  • the pressure-reducing means is a third orifice arranged at a location downstream of the pressure control valve.
  • the flow rate of the refrigerant gas is restricted by the third orifice, and hence the pressure of the refrigerant gas to be sent to the crankcase is lowered, whereby the pressure within the crankcase is prevented from being excessively increased.
  • a fourth passage for guiding the refrigerant gas at the location downstream of the pressure control valve and upstream of the pressure-reducing means to the discharge control valve has a fourth orifice provided in an intermediate portion thereof, a cross-sectional passage area of the third orifice being smaller than a cross-sectional passage area of the fourth orifice.
  • the flow rate of the refrigerant gas flowing through the fourth passage is restricted by the fourth orifice, whereby an impact of the refrigerant gas acting on the discharge control valve when the refrigerant gas flows into the discharge control valve is reduced.
  • damage to the discharge control valve is reduced, which improves the durability and reliability of the compressor.
  • the first passage has a portion formed by a hole formed through an annular element fixedly fitted on the rotational shaft.
  • the swash plate is brought into contact with the annular element when the inclination angle of the swash plate becomes minimum, since the annular element rotates in unison with the swash plate, abrasion of the swash plate can be reduced compared with a case of the swash plate being brought into contact with the housing or an annular element fixed to the housing.
  • the third passage includes a front head-side passage for communicating between a front head-side bearing-receiving space defined on a front head-side portion of the rotational shaft, for receiving a shaft seal and a front head-side bearing therein, and the crankcase, a rotational shaft-side passage for communicating between a rear head-side bearing-receiving space defined on a rear head-side portion of the rotational shaft, for receiving a rear head-side bearing therein, and the front head-side bearing-receiving space, and a rear head-side passage communicating between the rear head-side bearing-receiving space and the suction chamber.
  • a front head-side passage for communicating between a front head-side bearing-receiving space defined on a front head-side portion of the rotational shaft, for receiving a shaft seal and a front head-side bearing therein, and the crankcase
  • a rotational shaft-side passage for communicating between a rear head-side bearing-receiving space defined on a rear head-side portion of
  • the bearings and the shaft seal are lubricated and cooled by lubricating oil contained in the gas flowing through the third passage, so that it is possible to prevent seizure of the component parts.
  • FIG. 1 is a longitudinal cross-sectional view of a clutchless variable capacity awash plate compressor according to an embodiment of the invention, in a state of a refrigerant outlet passage thereof being open, and FIG. 2 is an enlarged partial view showing this state of the compressor.
  • FIG. 3 is a longitudinal cross-sectional view of the clutchless variable capacity swash plate compressor in a state of the refrigerant outlet passage being closed, and FIG. 4 is an enlarged partial view showing this state of the compressor.
  • the clutchless variable capacity swash plate compressor has a cylinder block 1 having one end thereof secured to a rear head 3 via a valve plate 2 and the other end thereof secured to a front head 4.
  • the cylinder block 1 has a plurality of cylinder bores 6 axially extending therethrough at predetermined circumferential intervals about a shaft (rotational shaft) 5.
  • Each cylinder bore 6 has a piston 7 slidably received therein.
  • the front head 4 defines therein a crankcase 8 in which a swash plate 10 is received.
  • a plurality of shoes 50 each supporting one end 11a, spherical in shape, of a corresponding one of connecting rods 11 in a relatively rollable manner with respect to the shoe 50 are retained on a sliding surface 10a of the swash plate 10 by a retainer 53.
  • the retainer 53 is mounted on a boss 10b of the swash plate 10 via a radial bearing 55 in a relatively rotatable manner with respect to the swash plate 10.
  • the radial bearing 55 is prevented from falling off by a stopper 54 fixed to the boss 10b by a screw 45.
  • the connecting rod 11 has the other end portion 11b thereof secured to a corresponding one of the pistons 7.
  • Each of the shoes 50 is comprised of a shoe body 51 relatively rollably supporting a front surface of the one end 11a of the connecting rod 11 and a washer 52 for relatively rollably supporting a rear surface of the one end 11a of the same.
  • the suction chamber is arranged such that it surrounds the discharge chamber 12.
  • the rear head 3 is formed with a suction port (not shown) for communication with an outlet port of an evaporator (not shown).
  • FIG. 2 is an enlarged cross-sectional view showing the state of the refrigerant outlet passage 39 being opens while FIG. 4 is an enlarged cross-sectional view showing the state of the refrigerant outlet passage 39 being closed.
  • a check valve (discharge control valve) 31 is arranged in an intermediate portion of the refrigerant outlet passage 39 for communication between the discharge chamber 12 and a discharge port 1a.
  • the refrigerant outlet passage 39 includes a passage 39a formed in the rear head 3 and a passage 39b formed through a valve plate 2.
  • the passage 39b is in communication with the discharge port 1a formed in the cylinder block 1.
  • the check valve 31 in the form of a bottomed hollow cylinder has a spring (urging member) 32 received therein.
  • the spring 32 has one end thereof held in contact with a stopper 56 fixed to the rear head 3 by a cap 59 and the other end thereof held in contact with the bottom of the check valve 31.
  • a space 33 within the check valve 31 is in communication with the crankcase 8 via a passage 34.
  • the urging force of the spring 32 and a pressure from the crankcase 8 act on one side (upper side) of the check valve 31 in a valve-closing direction (i.e. a direction for decreasing the valve opening).
  • a valve-closing direction i.e. a direction for decreasing the valve opening.
  • the check valve 31 moves in the valve-opening direction to close the refrigerant outlet passage 39, whereby only the pressure from the discharge chamber 12 acts on the lower side of the check valve 31 in the valve-opening direction. That is, the pressure from the discharge port 1a ceases to act on the lower side of the check valve 31.
  • a control valve (pressure control valve) 81 is arranged in an intermediate portion of the passage 57.
  • a solenoid (not shown) of the control valve 81 is energized to seat a valve element 81b on a valve seat, whereby the second passage 57 is closed, whereas when the thermal load becomes low, the solenoid is deenergized to cause the valve element 81b to move away from the valve seat, whereby the second passage 57 is opened.
  • the operation of the control valve 81 is controlled by a computer, not shown.
  • the suction chamber 13 and the crankcase 8 communicate with each other via a first passage 58.
  • the first passage 58 includes an orifice (second orifice) 58a formed through the valve plate 2, a passage 58b formed in the cylinder block 1, and a hole 58c formed in a ring (annular element) 59.
  • the suction chamber 13 and the crankcase 8 communicate with each other via a third passage 60.
  • the third passage 60 includes a passage 60a formed in the front head 4, a front head-side bearing-receiving space 60b formed in the front head 4, a passage 60c formed through the shaft 5, a rear head-side bearing-receiving space 60d formed in the cylinder block 1, the passage 58b formed in the cylinder block 1, and the orifice 58a formed through the valve plate 2.
  • the passage 58b formed in the cylinder block 1 and the orifice 58a formed through the valve plate 2 form part of the first passage 58 as well as part of the third passage 60.
  • the passage 60c has a rear head-side end portion formed with an internal thread 61 into which a screw 62 is screwed.
  • the screw 62 is formed therethrough with an orifice (first orifice) 62a.
  • the passage area of the orifice 62a is smaller than that of the orifice 58a of the valve plate 2 which forms part of the first passage 58. Therefore, only when the boss 10b of the swash plate 10 substantially closes the hole 58c of the ring 59 to substantially reduce the cross-sectional area of the first passage 58, refrigerant gas within the crankcase 8 is introduced into the suction chamber 13 through the third passage 60.
  • the valve plate 2 is formed with refrigerant outlet ports 16 for each communicating between a compression chamber 82 and the discharge chamber 12, and refrigerant inlet ports 15 for each communicating between a compression chamber and the discharge chamber 12.
  • the refrigerant outlet ports 16 and the refrigerant inlet ports 15 are arranged at predetermined circumferential intervals about the rotational shaft 5.
  • the refrigerant outlet ports 16 are opened and closed by respective discharge valves 17.
  • the discharge valves 17 are fixed to a rear head-side end face of the valve plate 2 by a bolt 19 and nut 20 together with a valve stopper 18.
  • the refrigerant inlet ports 15 are opened and closed by respective suction valves 21, which are arranged between the valve plate 2 and the cylinder block 1.
  • a rear end of the rotational shaft 5 is rotatably supported by a radial bearing (rear head-side bearing) 24 and a thrust bearing (rear head-side bearing) 25, both received in the rear head-side bearing-receiving space 60d, while a front end of the rotational shaft 5 is rotatably supported by a radial bearing (front head-side bearing) 26 which is received in the front head-side bearing-receiving space 60b.
  • a radial bearing front head-side bearing
  • the cylinder block 1 has a central portion thereof formed with an internal thread 1b into which an adjust nut 83 is screwed.
  • the shaft 5 is preloaded via the thrust bearing 25 by tightening the adjust nut 83. Further, a pulley (not shown) is fixedly fitted on the front end portion of the shaft 5.
  • the shaft 5 has a thrust flange 40 rigidly fitted thereon for transmitting torque of the shaft 5 to the swash plate 10.
  • the thrust flange 40 is supported on an inner wall of the front head 4 by a thrust bearing 33.
  • the thrust flange 40 and the swash plate 10 are connected with each other via a hinge mechanism 41, whereby the swash plate 10 can tilt with respect to an imaginary plane perpendicular to the rotational shaft 5.
  • the swash plate 10 is slidably and tiltably fitted on the shaft 5.
  • the hinge mechanism 41 is comprised of a bracket 10e formed on a front surface 10c of the swash plate 10, a linear guide groove 10f formed in the bracket 10e, and a rod 43 screwed into a swash plate-side surface 40a of the thrust flange 40.
  • the longitudinal axis of the guide groove 10f is inclined at a predetermined angle with respect to the front surface 10c of the swash plate 10.
  • the rod 43 has one spherical end 43a thereof slidably fitted in the guide groove 10f.
  • Torque of an engine, not shown, installed on an automotive vehicle, not shown, is constantly transmitted to the pulley, not shown, and the shaft 5 to rotate the same. Torque of the shaft 5 is transmitted to the awash plate 10 via the thrust flange 40 and the hinge mechanism 41 to cause rotation of the swash plate 10.
  • the rotation of the swash plate 10 causes the shoes 50 to relatively rotate along the sliding surfaces 10a of the swash plate 10, whereby the torque transmitted from the swash plate 10 is converted into the reciprocating motion of each piston 7.
  • the piston 7 reciprocates within the cylinder bore 6 associated therewith, the volume of a compression chamber 82 within the cylinder bore 6 changes.
  • suction, compression and delivery of refrigerant gas are sequentially carried out in the compression chamber 82, whereby refrigerant gas is delivered from the compression chamber 82 in an amount corresponding to the inclination of the swash plate 10.
  • the suction valve 21 opens to draw low-pressure refrigerant gas from the suction chamber 13 into the compression chamber 82 within the cylinder bore 6.
  • the discharge valve 17 opens to deliver high-pressure refrigerant gas from the compression chamber 82 into the discharge chamber 12.
  • the compressor is constructed such that the pressure from the crankcase 8 acts on the one side of the check valve 31 serving as a discharge control valve and the pressure from the discharge chamber 12 acts on the other side of the same, and a spring having a relatively small spring force is employed as the spring 32 for urging the check valve 31 in the valve-closing direction. Therefore, even when the pressure within the discharge chamber 12 is progressively reduced with decrease in the thermal load, the check valve 30 is kept open until the compressor enters the minimum piston stroke condition (extremely low-load operating condition) in which the swash plate 10 reduces the passage area of the first passage.
  • the solenoid of the control valve 32 is energized to cause the plunger 81d to move in the valve-closing direction, whereby the valve element 81b moves in the valve-closing direction by the urging force of the spring 81c to close the second passage 57.
  • the high-pressure refrigerant gas is inhibited from flowing from the discharge chamber 12 into the crankcase 8, whereby the pressure within the crankcase 8 is lowered to increase the inclination of the swash plate 10.
  • the boss 10b of the swash plate 10 moves away from the hole 58c of the ring 59, whereby the first passage 58 is fully opened.
  • the refrigerant gas within the crankcase 8 flows into the suction chamber 13 via the first passage 58, so that lowering of the pressure within the crankcase 8 is accelerated.
  • the passage area of the first passage 58 is maximized, the refrigerant gas hardly flows into the suction chamber 13 through the third passage 60.
  • the clutchless variable capacity swash plate compressor provides the following effects:
  • the suction chamber 13 can be arranged at a location radially outward of the discharge chamber 12, which facilitates control of sealing of the compressor against the outside air. Further, it is possible to avoid the event of the spring for preloading the shaft 5 being freely rotated following the rotation of the shaft 5 and wrung off to make it impossible to open/close the suction port 3a, so that the reliability of the compressor can be enhanced.
  • a mechanism e.g. the transmission cylinder and the blocking member in the prior art
  • check valve 31 as a discharge control valve makes it possible to simplify the construction of the compressor.
  • the compressor is constructed such that the pressure within the crankcase 8 is caused to act on the one side of the spool valve 31 serving as a discharge control valve, while the pressure within the discharge chamber 12 is caused to act on the other side of the check valve 31, so that a spring having a relatively small spring force can be used as the spring 32 for urging the check valve 31 in the valve-closing direction.
  • a spring having a relatively small spring force can be used as the spring 32 for urging the check valve 31 in the valve-closing direction.
  • a clutchless variable capacity swash plate compressor constructed such that pressure within a suction chamber is caused to act on one side of a check valve, while pressure within a discharge chamber is caused to act on the other side of the same, since the differential pressure between the suction chamber and the discharge chamber is large, it is required to use a spring having a relatively large spring force as a spring for urging the check valve in the valve-closing direction. Further, the pressure within the suction chamber largely change according to changes in thermal load.
  • the check valve when the pressure within the discharge chamber is progressively lowered with decrease in thermal load, the check valve sometimes operates to close a refrigerant outlet passage before the compressor enters the minimum piston stroke condition, thereby undesirably inhibiting refrigerant gas from flowing toward a condenser via a discharge port.
  • the present embodiment provides a solution to this problem.
  • the bearings 26, 24, 25 and the shaft seal 46 are lubricated and cooled by lubricating oil contained in the refrigerant gas passing through the third passage 60.
  • check valve 31 is used as a discharge control valve
  • another kind of valve such as a spool valve or a rotary valve may be employed in place of the check valve.
  • FIG. 5 is a longitudinal cross-sectional view of a clutchless variable capacity swash plate compressor according to another embodiment of the invention, in a state of a refrigerant outlet passage being closed.
  • FIG. 6 is an enlarged partial view of the FIG. 5 clutchless variable capacity swash plate compressor, showing the state of the refrigerant outlet passage being closed
  • FIG. 7 is an enlarged partial view of a rear head of the FIG. 5 clutchless variable capacity swash plate compressor, showing the state of the refrigerant outlet passage being open.
  • FIG. 8 is an enlarged partial view of another cross section of the rear head of the FIG. 5 clutchless variable capacity swash plate compressor, in which a fourth passage is shown.
  • This embodiment is distinguished from the above embodiment in which the refrigerant gas within the crankcase 8 is guided toward the one side of the check valve 31 serving as a pressure control valve, to thereby close the pressure control valve, in that refrigerant gas within a discharge chamber 112 is directly guided toward one side of a check valve 131 serving as a discharge control valve, to thereby close the pressure control valve, as described in detail hereinbelow.
  • FIGS. 5 to 8 Component parts and elements similar to those of the above embodiment are designated by identical reference numerals, and detailed description thereof is omitted.
  • the check valve 131 is arranged in an intermediate portion of a refrigerant outlet passage 139 for communicating between the discharge chamber 112 and a discharge port 1a.
  • the refrigerant outlet passage 139 includes a passage 139a formed in a rear head 103 and a passage 39b formed through a valve plate 2.
  • the passage 139b is continuous with the discharge port 1a formed in a cylinder block 1.
  • a spring (urging member) 132 Received in the check valve 131 in the form of a bottomed cylinder is a spring (urging member) 132 having one end thereof held in contact with an annular holder 56 and the other end thereof held in contact with the bottom of the check valve 31.
  • a rear head 103 has a cap 159 fixedly attached thereto, and the annular holder 56 is urged against the cap 159 by the urging force of the spring 132.
  • a space 133 within the check valve 131 is in communication with a crankcase 8 via a passage 134.
  • the urging force of the spring (urging member) 132 and the pressure of refrigerant gas guided through the fourth passage 71 act on one side (upper side) of the check valve 131 in a valve-closing direction (direction for decreasing a valve opening).
  • the check valve 131 When the check valve 131 is open, the discharge port 1a and the discharge chamber 112 are in communication with each other via the refrigerant outlet passage 139. Therefore, the pressure from the discharge port 1a and the pressure the discharge chamber 112 act on the other side (lower side) of the check valve 131 in a valve-opening direction (direction for increasing the valve opening).
  • the check valve 131 moves in the valve-closing direction to close the refrigerant outlet passage 139, whereby only the pressure from the discharge chamber 112 acts on the lower side of the check valve 131. That is, the pressure from the discharge port 1a is inhibited from acting on the lower side of the check valve 131.
  • a control valve (pressure control valve) 81 In an intermediate portion of the passage 157, there is arranged a control valve (pressure control valve) 81.
  • an orifice (third orifice) 70 is provided in the second passage 157 at a location downstream of the control valve 81 as pressure-reducing means for reducing pressure of refrigerant gas guided from the discharge chamber 112 to the crankcase 8.
  • a solenoid, not shown, of the control valve 81 When thermal load on the compressor becomes high, a solenoid, not shown, of the control valve 81 is energized, whereby a valve element 81b is seated on a valve seat to close the second passage 157, whereas when the thermal load becomes low, the solenoid of the control valve 81 is deenergized, whereby the valve element 81b moves away from the valve seat to open the second passage 157.
  • the operation of the control valve 81 is controlled by a computer, not shown.
  • a portion 157a formed in the second passage 157 at a location downstream of the control valve 81 and upstream of the orifice 70, and the space 133 within the check valve 131 are in communication with each other via the fourth passage 71 formed in the rear head 103.
  • an orifice (fourth orifice) 72 In an intermediate portion of the fourth passage 71, there is mounted an orifice (fourth orifice) 72. The flow rate of refrigerant gas guided into the space 133 within the check valve 131 through the fourth passage 71 is reduced by the orifice 72.
  • the first orifice 70 is smaller than the orifice 72 in cross-sectional passage area.
  • a first passage 158 includes a passage 158a formed through the valve plate 2, a passage 58b formed in the cylinder block 1, and a hole 58c formed in a ring 59 fixedly fitted on a shaft 5.
  • the present embodiment is distinguished from the FIG. 1 embodiment in that the passage 158a formed through the valve plate 2 is not an orifice.
  • a third passage 60 includes a passage 60a formed in the front head 4, a front head-side bearing-receiving space 60b formed in the front head 4, a passage 60c formed through the shaft 5, a rear head-side bearing-receiving space 60d formed in the cylinder block 1, the passage 58b formed in the cylinder block 1, and the passage 158a formed through the valve plate 2.
  • the passage 58b formed in the cylinder block 1 and the passage 158a formed through the valve plate 2 form part of the first passage 58 as well as part of the third passage 60.
  • the solenoid of the control valve 81 is deenergized to cause a plunger 81d to move in the valve-opening direction, whereby the valve element 81b moves in the valve-opening direction against the urging force of a spring 81c to open the second passage 157.
  • high-pressure refrigerant gas flows from the discharge chamber 112 to the crankcase 8 via the second passage 157.
  • the flow rate of the refrigerant gas delivered to the crankcase 8 is limited by the orifice 70, and the pressure of the refrigerant gas is lowered.
  • the pressure within the crankcase 8 is progressively increased by the high-pressure refrigerant gas from the discharge chamber 112 to decrease the inclination angle of a swash plate 10.
  • a boss 10b of the swash plate 10 substantially closes the hole 58c of the ring 59.
  • the cross-sectional area of the first passage 58 is substantially reduced, whereby lowering of the pressure within the crankcase 8 is suppressed.
  • High-pressure refrigerant gas at a location downstream of the control valve 81 and upstream of the orifice 70 is sent to the space 133 within the check valve 131 via the fourth passage 71.
  • the boss 10b of the swash plate 10 substantially closes the hole 58c of the ring 59 as described above, to substantially reduce the cross-sectional area of the first passage 58, the refrigerant gas within the crankcase 8 flows into the suction chamber 13 through the third passage 60. This prevents an excessive increase in the pressure within the crankcase 8, and at the same time allows the refrigerant gas to circulate within the compressor.
  • the compressor When the compressor is in a minimum piston stroke condition (i.e. a state shown in FIG. 5), the refrigerant gas which flows out from the suction chamber 113 sequentially passes through the compression chamber 82, the discharge chamber 112, the second passage 157, the crankcase 8, and the third passage 60, and returns to the suction chamber 113.
  • a minimum piston stroke condition i.e. a state shown in FIG. 5
  • the control valve 81 is closed to block the second passage 157.
  • the high-pressure refrigerant gas is inhibited from flowing from the discharge chamber 112 into the crankcase 8, whereby the pressure within the crankcase 8 is progressively decreased to increase the inclination angle of the swash plate 10. Further, the pressure of the refrigerant gas guided into the space 133 within the check valve 131 through the fourth passage 71 is also lowered.
  • the clutchless variable capacity swash plate compressor according to the present embodiment provides the same effects as obtained by the compressor of the preceding embodiment, as well as the following effects:
  • the refrigerant gas in the discharge chamber 112 is directly introduced into the one side (i.e. the space 133) of the check valve 131 to drive the same, the responsivity of the check valve 131 is improved. As a result, the delivery quantity of the refrigerant gas (i.e. the capacity of the compressor) can be changed promptly, which makes it possible to obtain a more agreeable air-conditioned state by cooling.
  • the check valve 131 is capable of operating reliably to reduce the refrigerating capacity of the compressor to zero, it is not required to set the pressure within the crankcase 8 at a higher level by reducing the cross-sectional area of the first communication passage 58. Therefore, damage to component parts, such as the retainer 53 for pulling the pistons 7 within the crankcase 8, the shaft seal 46 for preventing the outside air from flowing into the crankcase 8, and so forth, is reduced, which improves the durability and reliability of the compressor.
  • the orifice 72 is arranged in the intermediate portion of the fourth passage 71, when the control valve 81 opens to allow the high-pressure refrigerant gas to flow toward the space 133 within the check valve 131, the flow rate of the refrigerant gas is restricted by the orifice 72, whereby an impact of the refrigerant gas acting on the check valve 131 is reduced.
  • bearings 24, 25 are lubricated and cooled by the lubricating oil contained in the refrigerant gas.
  • the single passage 71 is formed as the fourth passage, a plurality of passages may be formed for the purpose.
  • the single orifice (orifice 70) is mounted as pressure-reducing means, a plurality of orifices may be used, or alternatively, the second passage 157 may be formed to have an intermediate portion reduced in cross section, instead of mounting an orifice 70 as another pressure-reducing means.
  • the check valve 131 is used as a discharge control valve, a spool valve, a rotary valve, not shown, or the like may be employed in place of the check valve 131.
  • the clutchless variable capacity swash plate compressor according to the invention is suitable for use as a refrigerant compressor for an air-conditioning system for an automotive vehicle.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
EP99925334A 1998-06-16 1999-06-16 Compresseur sans embrayage du type a plateau oscillant a deplacement variable Withdrawn EP1088991A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP18558298 1998-06-16
JP18558298 1998-06-16
PCT/JP1999/003203 WO1999066203A1 (fr) 1998-06-16 1999-06-16 Compresseur sans embrayage du type a plateau oscillant a deplacement variable

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EP1088991A1 true EP1088991A1 (fr) 2001-04-04

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EP99925334A Withdrawn EP1088991A1 (fr) 1998-06-16 1999-06-16 Compresseur sans embrayage du type a plateau oscillant a deplacement variable

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EP (1) EP1088991A1 (fr)
WO (1) WO1999066203A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1715263A3 (fr) * 2005-04-21 2007-09-12 Behr GmbH & Co. KG Dispositif de climatisation, en particulier pour véhicule automobile
CN102472268A (zh) * 2009-07-06 2012-05-23 开利公司 用于压缩机容量控制的旁路卸载阀

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040062660A1 (en) * 2001-01-29 2004-04-01 Yukio Kazahaya Variable displacement type swash plate clutch-less compressor
US7014428B2 (en) 2002-12-23 2006-03-21 Visteon Global Technologies, Inc. Controls for variable displacement compressor

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3254853B2 (ja) * 1993-11-05 2002-02-12 株式会社豊田自動織機 クラッチレス片側ピストン式可変容量圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9966203A1 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1715263A3 (fr) * 2005-04-21 2007-09-12 Behr GmbH & Co. KG Dispositif de climatisation, en particulier pour véhicule automobile
CN102472268A (zh) * 2009-07-06 2012-05-23 开利公司 用于压缩机容量控制的旁路卸载阀
CN102472268B (zh) * 2009-07-06 2017-11-03 开利公司 用于压缩机容量控制的旁路卸载阀

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